goodwillie



Jan. 31, 1956 J. E. GOODWILLIE 2,733,019

WINDER MACHINE Filed Oct. 15, 1955 3 Sheets-Sheet l IHFE 7222:?

MM M John 5', Gaoa'aa'l/Ze b H .4114) H I ZL 7775 Jan. 31, 1956 .1. E.GOODWILLIE WINDER MACHINE 3 Sheets-Sheet 2 Filed Oct. 15, 1953 l M v////a Jan. 31, 1956 J. E. GOODWILLIE 2,733,019

WINDER MACHINE Filed Oct. 15, 195:5 s Sheets-Sheet 3 a wi HgZ i E UitedStates Patent C) WINDER MACHINE John E. Goodwillie, Beloit, Wis.,assignor to Beloit Iron Works, Beloit, Wis., a corporation of WisconsinApplication October 15, 1953, Serial No. 386,171 '8 Claims. (Cl. 242-66)This invention relates to a machine for winding web material, such aspaper, to produce a roll of the desired hardness irrespective of theweight of the roll. In particular, the invention deals with a drumwinder adapted to produce very soft rolls of paper, such as crepedtissue paper, without being influenced by the weight of the roll beingwound.

Drum winders characteristically produce Wound rolls of web materialwhich increase in hardness as the weight of the roll increases. Priorattempts to counterbalance the weight of the roll being wound have notbeen successful, particularly because of the difliculty of controllingthe operation. Another difiiculty which arose because the roll liftingforce must be applied to the projecting end portions of the shaft onwhich the roll is being wound and, since this shaft must be ofrelatively small diameter in comparison with its length, deflection ofthe shaft and the roll occurred. As a result of this, the centralportion of the roll was not benefited by such lifting, and unevenwinding was obtained. This latter difliculty has now been cured by theuse of certain anti-deflection roll assemblies, which are described andclaimed in United States application Serial No. 233,657, owned by theassignee of this application, filed June 26, 1951, and since issued asU. S. Patent No. 2,654,546. Controlled lifting of the shaft has,however, presented an additional unsolved problem to the art.

According to this invention, a drum winder is equipped with fluidpressure operated jacks acting on "the ends of the winder shaft torelieve some of the load of the roll being wound from the winder drums,and control means are provided for the fluid pressure operated jackswhich respond to the continuously increasing weight of the roll beingwound upon the shaft.

It is, therefore, an important object of the instant invention toprovide an improved winder drum assembly.

A further object of the instant invention is to provide an improvedwinder drum assembly wherein improved control means continuously sensingthe increase in roll size and weight actuate fluid pressure mechanism tocontinuously change the lifting forces acting upon the ends of theshaft.

It is a further object to provide, in a winder machine of the underdrumtype, in combination, a winder drum, a winder shaft carrying atransverse load urging the shaft toward the drum, bearing meansrotatably receiving the ends of the shaft, fluid pressure actuated meansengaging the bearing means and urging the bearing means and shaftreceived thereby away from the drum, and means responsive to apredetermined function of the distance between the shaft and the drum incontrol of the fluid pressure actuated means tending to urge the shaftaway from the drum.

Still another object of the instant invention is to pro vide improvedmechanism for controlling the load supported by a pair of winder drumsin a web drum winder while a web roll is continuously building up on awinder shaft cooperating with the winder drums to support the to a crossshaft 22 which I leased from the ratchet 27 so as to roll, whichcomprises a pair of fluid pressure actuated supports rotatably carryingopposite ends of the shaft, valve means in control of actuating fluidpressure supplied to said supports, a cam rotating in response tomovement of the shaft away from the winder drums during roll build up,and follow-up mechanism engaging said cam and operating said valve meansin response to a predetermined function of said movement.

Other features, objects and advantages of the present invention willbecome apparent to those skilled in the art from the following detaileddisclosure thereof with reference to the annexed sheets of drawingswhich, by way of a preferred embodiment only, illustrate one windermachine according to this invention.

On the drawings:

Figure 1 is a broken front in vertical cross-section, of a to thisinvention;

Figure 2 is an end elevational view of the machine of Figure 1;

Figure 3 is a detailed cross-sectional elevational view of a controlvalve used in the instant invention (and shown diagrammatically inFigure 4); and

elevational view, with parts winder machine according Figure 4 is adiagrammatical view showing the con-' trol mechanism employed in theinstant device.

As shown on the drawings:

As shown in Figures 1 and 2, the winder machine 10 of this inventionincludes side frames 11, 11 carrying bearing supports for rotatablymounting a pair of spaced horizontally aligned winder drums 12, 12coacting to define a winder nip 13 therebetween, which is substantiallyvertically aligned. Upstanding end frame portions 11a, 11a carryvertical tracks 14, 14 in which are slidably mounted carriages 15, 15each having a split bearing clamp 16 at the lower end thereof projectinginto alignment with the winder nip 13 beyond the ends of the winderdrums 12, 12. The carriages 15, 15 have bosses 15a, 15a on the rearfaces thereof slidably receiving mounting pins 17, 17

The pin 17 has heads 17a, of and compression springs 18, 18 are disposedaround the pin 17 between these heads 17a, 17a and the adjacent ends ofthe boss 15a. Each head 17a is pivotally connected at its outer end withthe end of a sprocket chain 19 that is trained around a bottom sprocket20 rotatably mounted on the frame portion 111! and a top sprocket 21secured is rotatably mounted on the end The shaft 22 is rotated by meansone end thereof driven by a chain actuated from a sprocket 25 on a shaft26 carried by the end frame. a ratchet 27 engaged by a pawl 28. The pawl28 can be disengaged from the ratchet by raising a lever 29. The lever29 is conveniently actuated by the end of the rod 30 which is raised andlowered from a foot pedal 31 pivoted 0n the bottom of the frame 11. Thehand wheel actuated shaft 26 is operative to rotate the cross shaft 22in the direction for causing the sprocket 21 to drive the chains 19 for,raising the carriages 15 in their tracks The pawl 28 is effective tohold the shaft 22 against rotation in the opposite direction but can bere permit this opposite rotation. The springs 18 serve to form resilientsupports for the carriages 15 on the sprocket chain 19. The bearingclamps 16 carried by the carriages, therefore, have spring mountings onthe lifting chains.

The frames 11, 11 also carry vertical jack cylinders 32a and 32b withpistons 33:: and 33b, respectively, slidable therein and actuatingpiston rods 34a and 34b, respectively, which project out of the opentops thereof. The upper ends of the piston rods 34a and 34b arepivotally connected to the bearing clamps 16 on the carriages 15,

frame portions 11a. of a sprocket 23 on 24 "which, in turn, is handwheel operated The shaft 26 carries 17a at opposite ends there I A fluid(which may be a gas such as air or a liquid such as water) underpressure is admitted into the bottom ends of the jack cylinders 32a and32b through the pipes 35a and 35b, respectively, fed from the valves 36aand raise the bearing clamps 16, 16.

A paper web W is fed to the nip 13 around the underside of one of thewinder drums 12. As shown in Figure 2, the web W is directed into thewinder machine around the top of a roll 37 and over an adjustable guidebar 38 which laps the web around the underside of the first winder drum12.

' An ejector roll 39 for pushing a wound paper roll' out of the'nip 13is carried on gear segments 40 at the ends of the first underdrum 12 andis swingable over the roll 12. Pinion gears 41 in engagement with thearcuate gear segment 48 are effective to swing the roll 39 through thenip 13 to eject the wound roll. 7

The split bearing clamps 16, 16 surround the winder shaft bearings 42,42 on the ends of the winder shaft 43. As best shown in Figure 2, thebearing clamps 16 are split so as to be quickly engaged on the bearingportions of the shaft bearings 42. Each bearing clamp 16 includes afixed lower half portion 16a on the carriage and a swingable top halfportion 1612 which is pivoted on a pin 16c carried by the carriage 15. Akeeper 16d on the free end of the swingable bearing portion 16b engagesa latch 'or locking dog 44 which is pivoted on a pin 45 carried by thelower half 16a of the clamp. A spring 46 urges the latch 44 against thekeeper 16a to lock the two halves 16a and 1611 together. An operatinghandle 47 on the lower end of the latch 44, however, is adapted todepress the spring 46 for releasing the latch 44 from the keeper 16d. Ahandle 43 is provided on the swingable section 16b to raise and lowerthe section for opening and closing the clmp.

As hereinbefore mentioned, the details of the anti-deflection rollassembly mounted on the shaft 43 form part of the invention disclosedand claimed in application Serial No. 233,657, filed June 26, 1951, nowU. S. Patent No. 2,654,546, and as such do not form the subject matterof the instant invention. The instant invention is adapted for the useof any anti-deflection assembly for the shaft 43 and preferably thatdescribed in said U. S. Patent No. 2,654,546, wherein the bearings 42have segmental spherical cap receiving portions which are adapted totilt in the clamps 16, 16 to provide a self-aligning bearing connection,and the shaft 43 itself comprises a tubular axle 49 with stub shafts43a, 43a at opposite ends mounting the bearings 42 and with acylindrical shell 50 surrounding the tubular axle in spaced concentricrelation mounted on the axle by a pair of rubber (or similar solidelastomeric material) mountings 51 adjacent to but inwardly spaced fromthe opposite ends of the shell 50, so as to substantially preventdistortion or deflection of the shell 50 even though the tubular axle 49portion is deflected slightly by a load. Also, a cardboard core 52 isusually slipped over the shell to actually receive the paper being woundthereabout.

In the operation of the winder machine 10 of this invention, the paper Wis fed under the first underdrum 12 as explained hereinbefore and isdirected upwardly into the nip 13. A winder tube or core is suitablyclamped in position on the shaft assembly 43. As indicated at thelocation of the broken away portion of the winder drum 12 in Figure 1,the tubular axle 49 of the shaft assembly 43 has mounted thereon aconcentric shell 50 resiliently carried on a rubber annulus 51 and acardboard core52 may be slid thereover. The winder shaft 43 has the endbearings 42 thereof mounted in the bearing clamp 16 and the carriages 15are loweredsuificiently so that the winding tube 52 on the shaft 43 willrest in the nip in engagement with both the drums 12, 12. In order tolower the eration.

winder shaft 43, fluid in the cylinders 32a and 32b is exhausted and thefoot pedal 31 is depressed to permit the hand wheel to be swung in adirection for lowering the carriages 15, 15. The leading end of thepaper web is then threaded around the winding tube 52. The leading endof the paper web is then clamped to the shell 50, and the drums 12, 12are driven to rotate the shaft assembly 42 so that a roll of paperbuilds up on the shaft assembly 43 in contact with the underdrums 12,12.

It will be understood that, as the roll increases in diameter, thewinder shaft assembly 43 rises in the nip 13 and the weight of the rollincreases, thereby increasing the pressure relationship between thepaper and the winder drums 12, 12. In order to relieve the weight of theroll from the winder drums 12, 12 so as to maintain a desired pressurerelation-ship between the paper being wound and the winder drums '12, 12air or other fluid under pressure is fed from the control unit, whichwill be described in detail in connection with Figures 3 and 4, throughthe pipes 35:: and 35b to the cylinders 32a and 32b under the pistons33a and 33b, respectively, for causing the piston rods 34:: and 34b toraise the bearing clamps 16, 16.

As the load of the roll being wound is transferred from the winder drums12, 12 to the fluid pressure jacks 32a and 3217, the tubular axleportion 49 of the winder shaft assembly 43 will be deflected somewhat.This deflection will be appreciable as the Weight of the roll increasesand as more and more of the roll weight is borne by the jacks 32a and32b acting through through the bearings at the ends of the shaftassembly 43. However, the shell 50 on the tubular axle 49, beingsupported inwardly from the ends thereof by the rubber collars 51, 51will only deflect in such a way as to prevent anytappreciable variationin pressure between the roll being wound and the winder drums along thelength of the roll.

The difliculty heretofore encountered in connection with an arrangementof this type was that the operators would often have difficulty inmaking the necessary adjustments to constantly correct the amount offluid pressure being used on the jacks 32a and 32b, so that a uniformpressure relationship between the roll being wound and the winder drumscould be maintained during the entire windup op- The instant inventionprovides a control arrangement which correlates the various functioningelements of this device and which is capable of continuously supplyingthe required fluid pressure to each of the jacks 32a and 32b. Thisdevice is shown diagrammatically in Figure 4.

As will be appreciated, as the roll builds up on the winder shaft 43,the winder shaft 43 rises up on the nip 13. The bearing clamps 16 willbe lifted therewith and the carriages 15 will rise in their tracks,causing the chains 19 to rotate the shaft 22 in a counterclockwisedirection. This shaft 22, in turn, drives the chain 24 to rotate theratchet 27 in a counterclockwise direction. The pawl 28 will notinterfere with the counterclockwise rotation of the ratchet 27 and thecarriages 15 can therefore rise in their tracks. In the instant device16, a cam 53 is also mounted on the shaft 22 at one extremity thereof,so that rotation of the shaft 22 also causes rotation of the cam 53, andthis rotation of the cam 53 takes place in response to movement of thewinder shaft 43 away from the winder drums 12. In fact, the position ofthe cam 53 depends upon the distance between the shaft 43 and the drums12, or the size of the roll on the shaft 43, or even the position of theshaft 43 (with respect to the other elements in the device 10).

The cam 53 has a cooperating follower or follow-up means 54 in the formof the arm 54 pivotally mounted at 55 and resiliently urged against theperipheral surface of the cam'53.

As will be explained in detail hereinafter, the cam 53 and follower 54form a part of the control mechanism which translates the distancebetween the shaft 43 and the drum '12 to roll size, then to roll weightand finally to fluid pressure required for the jacks 32a and 32b tocounteract 'a sufi'icient amount of the roll weight to maintain apredetermined pressure between the roll and the winder drum 12. TheWinder shaft 43 thus carries a transverse load in the form of the rollurging the shaft toward the drums 12; and the fluid pressure actuatedjacks 32a and 32b coact with the shaft bearings 42 to urge the shaft 43away from the drums 12, so that .the jacks 32a and 32b cooperate 'withthe drum 12 to carry the entire weight of the roll (as well as theweight of the shaft assembly 43). The actual relative positions of theshaft 43 and drums 12 are positions which are determined by the size ofthe roll being wound and these posi tions are substantially independentof the pressure between the roll and the drums '12 or the pressureexerted at the jacks 32a and 32b (unless such pressure were to exceedthe total weight of the roll and shaft 43). The cam 53 and follower 54(being suitably connected to the shaft 43 by follower mechanism such asthe sprocket chain 19, the shaft 22, etc.) operate in response to apredetermined function of the positional relationship between the shaft43 and the drums 12 'to actuate "the jacks 32a and 32b to the extentdesired.

Referring again to Figure 4, it will be seen that air under'pressureenters the control system through the supply line S and into a reservoirR. From the reservoir R the compressed air passes through a letdown'valve 56 which maintains a predetermined air pressure in the line 57leading to the control valve 58, as indicated by the air pressure gauge59. The follow-up arm 54 controls the flow of air through the controlvalve 58 and, as the cam 53 rotates in the direction indicated by thearrow, it urges the follow-up arm 54 in the open direction at anincreasing rate of speed per rate of angular rotation. In other words,as the distance between the shaft 43 and the winder arms 12 increasesthe cam 53 is rotated in the direction indicated by the arrow and suchrotation takes place as a linear function of the movement of the shaft43, but the periphery of the cam 53 is so designed that the follow-uparm 54 moves as a function of the square of this distance, was totranslate the distance between the-shaft 43 and "the drums 12 to rollsize, or the cross-sectional area of the roll. The movement of thefollow-up arm 54 controls the operation of the throttle valve 58, sothat the valve 58 releases an air pressure signal that is apredetermined function of the roll size. This signal then passes throughthe valve exit line 60 and into a control valve 61 of the type known asa .totalizer.

Figure 3 shows a sectional view of a valve which may functionas atotalizer in that it is capable of receiving an air signal andmultiplying or dividing this signal by a given factor and/or adding toor subtracting from this signal. As will be seen from Figure '3, air isfed from a constant pressure source in the header 62 through aflowcontrol valve, here shown as a needle valve 63 and into the actuatingpressure or operating pressure line 64, whence it goes to the device towhich it is to actuate. The stem 65 of the needle valve 63 isoperatively connected to separate diaphragms 66 and 67. Air pressurethrough the inlet line 68 acts against the bottom of the diaphragm 66and tends to open the valve 63; whereas air pressure'through the inletline 69 acts against the top of the diaphragm 67 and tends to close thevalve 63. Also, his-preferable to employ a'jumper 7ilfbetween theactuating air line 64 and the top side of the diaphragm 66. The jumper70 will tend to maintain the valve 63 in closed position when noactuating air is being received by the totalizer 61. As an example ofthe operation, if air of ten pounds pressure is received through theinlet 69 and air of fifteen pounds pressure is received through theinlet 68 the diaphragms will cooperate so as to open the valve 63 to theextent that the air pressure released to the actuating air line 64 isfive pounds. In other words, the air pressure released for operativepurposes is the difference between the air signals received. In likemanner, the air pressure released may be the total of the signalsreceived, merely by introducing the signals into the totalizer at theproper side of a diaphragm.

It will also be noted that the valve stem 65 is pivotally connected at71 to a lever arm '72 which has a pivot connection 73 midway between theends of the arm 72. A second actuating rod 74 comparable to theextension of the valve stem 65 is attached to the opposite end of thelever arm 72 by the pivot 75; and this actuating rod .74 has a pair ofdiaphragms 76 and 77 attached thereto. Air entering into the inlet 78beneath the diaphragm 76 urges the rod 74 upwardly and the valve 'stem65 downwardly by virtue of the lever arm 72; and air entering into theinlet 79 on top of the diaphragm '77 urges the rod 74 down and the valvestem 65 up in the same manner, so as to open the valve 63. 7

It will thus be seen that with the pivot 73 positioned in the middle ofthe lever arm '72, an air signal of five pounds going through the inlet68 and air signal of ten pounds going through .the inlet '79 will resultin the totaling of these two signals to obtain fifteen pounds pres- V bythe totalizer 61 is divided in two,

sure in the air signal going past the valve 63 into the actuating line64.

Multiplication and division of air signals may be effected usingtheinstant totalizer 61 'by movement of the pivot 73 in one direction oranother in the slot 8! and the lever arm 72. For example, if it isdesired to multiply a given signal by three, then the pivot 73 may beshifted to the right to the position 73' so as to effect a mechanicaladvantage at the lover of three to one for .air entering the inlet 79.Thus arranged, the totalizer 61 operates to receive three pounds airpressure at the inlet 79 and to release nine pounds actuating airpressure in the line 64. The setting of the pivot 73 may be donemanually in order to obtain the desired mechanical advantage (ordisadvantage) in the lever 72; and thus set, the totalizer 61 constantlyadds, subtracts, multiplies or divides the air signal or signalsreceived.

Referring again to Figure 4, the air signal in the throttle valve exitline 60 which is received by the totalizer-61 represents the size of theroll (in crossesec tional area) but each of the jacks 32a and 3211 .willcarry only approximately one-half of the total weight of the roll (whichis a linear function of the cross-sectional area), so the totalizer 61functions to divide the air signal received in half. This maybe done bymoving the pivot 73 to the left (in the drawing of Figure 3) so as toobtain a mechanical disadvantage of one to two for the air signalentering the inlet 79.

Referring again to Figure 4, the air signal received .so that actuatingair leaves the totalizer 61 in the line 81 with one-half the airpressure of the air in the line 60. The totalizer 61 is connected to anair source S" which feeds air under pressure through a filter F andintoheader 82, 'then through the constant pressure output valve 83 and into'the main header 84. From the main header 84 the air passes through thecontrol valve indicated at 85 for the totalizer 61. The header 84compares to the source line 62 of Figure 3, the valve .85 compares tothe valve 63 of Figure 3 and the actuating air outlet line 81 comparesto the outlet line 64 of Figure '3. The outlet air line 81 splits intotwo lines 81a" and 811; at the T 86, thereby 'initiat'ing the divisionor" controlling air to the twojacks 32a and 32b, respectively.

Tracing the a system the air in the inlet line 81a enters the totalizer87a which effectively translates the incoming air signal from roll sizeto roll weight. Actually, the incoming air signal indicates onlyone-half of the total cross-sectional area of the roll and the totalizer87a converts this to the weight of one-half of the roll, bymultiplyingthe received air'signal by a given factor, such as the factor .10, whichwill be determined on the basis of the type of paper and the compactnessof the winding of the roll. It will thus be seen that the source aircomes from the main header 84 through the line 84a and to the controlvalve 88a for the totalizer 87a, whereat it is translated to the inletair pressure from the line 81a times the predetermined factor for whichthe totalizer 87a is set. If set for the factor 10, then the air passingthrough the valve 88a and into the actuating air outlet 89a will have apressure of ten times the air entering through the inlet 81d.

The totalizer 87a also carries out an additional function, namely, thatof including an air signal which is representative of the weight of thewinder shaft assembly 43 (or approximately one-half of the weight ofthis assembly). This is done by passing the compressed air from theheader 84 through a throttle valve 90a which may be manually set toproduce a given air signal in the outlet line 91a which isrepresentative of one-half ofthe weight of the shaft assembly and theair signal in the line 91a is merely added to the product resulting fromthe multiplication of the air signal entering through the inlet line 81aby the weight factor.v Referring to Figure 3, it will be seen that thismay be accomplished by first setting the pivot 73 on the right side soas to obtain a mechanical advantage that is equal to the factor by whichthe air signal in the line 81a is to be multiplied. If this air signalis to be multiplied by ten then the pivot is moved to the right so as toobtain a mechanical advantage of ten to one in the lever 72 and theinlet air from the line 81a is directed into the inlet 79 (of Figure 3).The air signal in the throttle valve header 91a is, however, alreadybased upon weight and it is necessary only to add this air signal, andthis is accomplished by directing the air signal from the line 91a intothe inlet 68 of Figure 3, so that the totalizer may accomplishsimultaneously multiplication of one air signal and addition of another.

As previously indicated, the resulting air signal leav-' ing thetotalizer 87a is in the actuating air pressure line 89a; and thecompressed air therein passes through the valve 92a, the line 93a withthe gauge 94a therein, the valve 36a and the inlet line 35a for the jack32a.

The corresponding parts in the b system of Figure 4 are given the samereference numerals followed by the letter b and these elements functionin an identical manner. It will thus be seen that using the instantcontrol device on automatic the cam 53 and the follower 54 operate tocontinuously adjust the control device in response to changes in thedistance between the shaft 43 and the winder drum 12 so that theincreased weight of the roll is constantly compensated forautomatically. In addition, further adjustment may be employed using thethrottle valves 90a and 90b. These valves are originally set tocompensate for the share of the weight of the shaft assembly which theindividual jack must carry, but if during windup, it appears that oneside of the roll is being wound up more tightly than the other (forexample, because of irregularities in the thickness of the paper) themanual throttle valves 90a and 90b may be employed to make anadjustment, so that the amount of air being fed through these throttlevalves need not be the same.

It will be noted that the valves 92a and 92b are both set so as toafford direct communication between the lines 89a93a and 89b93b,respectively, for automatic control. When it is desired to put theinstrument on manual control, the valves 92a and 92b are shifted, forexample, by movement of the handle indicated symbolically at 94 to shiftthe handle 94 in the direction indicated by the arrow whereby the valves92a and 92b are each rotated 90 in the direction indicated by the arrow.

This results in cutting off the communication between the lines 89a and93a. and the lines 8% and 93b; and instead, communication at the valve92a is established between the line 93a and a jumper 95:: which connectsdirectly into the exit line 91a of the throttle valve 90a. In thismanner, the throttle valve 901: may be used as the sole parallel trackson said machine adjacent the ends of the 1 winder drums, awinder shaftextending along the length" 8 control for feeding actuating air pressurethrough the lines 91a, 95a, the valve 92a, the lines 93a and 35a intothe jack 32a. In like manner, the valve 92b is shifted by the samemovement which shifts the valve 92a and communication is thusestablished between the line 91b, the jumper 95b, and the line 93bleading through the valve 36b and the line 35b into the jack 32b. 7

The valves 36a and 36b serve to vent the jack 32a and 32b, respectivelythrough the lines 96a and 96b, respectively, the header 97 and the valve98. To accomplish this, the valve 36a is rotated in a counterclockwisedirection while the valve 98 is maintained in the position shown in thedrawing; and the valve 36b is rotated in a clockwise direction 90 toaccomplish the same thing.

It will be understood that modifications'and variations may be effectedwithout departing from the scope of the novel concepts of the presentinvention.

I claim as my invention:

1. A winder machine adapted to produce a wound roll of a controlleduniform degree of hardness irrespective of the weight thereof, whichcomprises a pair of under mounted on each end of the shaft andaccommodating.

relative tilting of the shaft and slidably retained in the,

tracks, separate and independent fluid pressure actuated support meansengaging the bearing means at opposite ends of the shaft for movementthereof in the tracks, means re-' sponsive to a predetermined functionof the distance between the shaft and the winding nip connected to eachof said support means for supplying actuating fluid pressure thereto andseparate and apart independently controlled inlet means connected toeach of said support means adapted to supply different amounts ofadditional actuating fluid pressure thereto.

2. A winder machine adapted to produce a wound roll ofa controlleduniformdegree of hardness irrespective of the weight thereof, whichcomprises a pair of under winder drums defining a vertical winding nip,upright parallel tracks on said machine adjacent the ends of theengaging the bearing means at opposite ends of the shaft for movementthereof in the tracks, said support meansv cooperating with the winderdrums to support the total Weight of the bearing means, shaft and roll,means re-- sponsive to a predetermined function of the roll sizesupplying actuating fluid pressure to each of said support means, andseparate and apart inlet means each responsive to a predeterminedfunction of the bearing and shaft weight connected to each of saidsupport means supplying v additional actuating fluid thereto.

3. A winder machine adapted to produce a Wound roll of a controlleduniform degree of hardness irrespective of the Weight thereof, whichcomprises a pair of under winder drums defining a vertical winding nip,upright of said winding nip for receiving the roll being woundthereabout, bearing means rotatably mounted on each end of the shaft andslidably retained in the tracks, separate and independent fluid pressureactuated support means engaging the bearing means at opposite ends ofthe shaft for movement thereof in the tracks, cam and follow-upmechanism connected to said shaft translating the distance from theshaft to the winding nip to a fluid pressure signal indicating therollsize, control means receiving said signal and translating the sameto actuating fluid pressure that is a predetermined function of the rollsize and supplying such actuating fluid pressure to each of saidsupports, and separate and apart inlet means each responsive to apredetermined function of the bearing and in said tracks, bearing clampscarried by said carriages adjacent the ends of said nip, upper and lowersprockets at opposite ends of each track, a lifting chain for eachcarriage trained around the adjacent upper and lower sprockets, lockingmeans for selectively locking the upper sprockets against rotation in adirection permitting lowering of the carriages, a fluid pressure jackadjacent each end of the nip, a piston rod projecting from each jackacting on the adjacent bearing clamp to raise and lower the clampsrelative to the nip, said winder shaft having bearings on the endsthereof receivable in said bearing clamps and accommodating relativetilting movement therebetween, a cam mounted for rotation with an uppersprocket, follow-up means engaging said cam, and valve means controlledby the follow-up means supplying actuating fluid pressure independentlyto each of said jacks for controlling the weight of the roll supportedby said winder drums.

5. Mechanism for controlling the load supported by a pair of winderdrums in a web drum winder while a web roll is continuously building upon a winder shaft cooperating with the winder drums to support the roll,which comprises bearing means rotatably carrying opposite ends of theshaft and movable therewith away from the Winder drums during roll buildup, fluid pressure actuated supports carrying said bearing means, a camconnected to said bearing means and rotating in response to movement ofsaid bearing means, follow-up means operatively engaging said cam, afirst control valve actuated by said foliow-up means, said cam andfollow-up means cooperating to translate bearing movement to a fluidpressure signal at the first control valve that is a predeterminedfunction of the roll size, a second control valve responsive to the rolldensity receiving the first control valve signal and translating thesame to a second signal that is a function of the roll weight, and fluidpressure inlet means for said supports being actuated by said secondcontrol valve.

6. Mechanism for actuating a pair of independent hydraulic jackscarrying opposite ends of a Winder shaft having a web roll continuouslybuilding up on the shaft and partially supported by under winder drums,which comprises a cam movable in response to movement of the shaft awayfrom the drums, follow-up means operatively engaging the cam, a firstcontrol valve actuated by the follow-up means to translate movement ofthe cam to a first fluid pressure signal that is a predeterminedfunction of the roll size, a second control valve responsive to the rolldensity receiving the first fluid pressure signal and translating thesame to a second signal that is a function of the roll weight, and fluidpressure inlet means for the jacks receiving the second signal to urgethe shaft away from the drums therewith.

7. Mechanism for actuating a pair of independent hydraulic jackscarrying opposite ends of a winder shaft having a web roll continuouslybuilding up on the shaft and partially supported by under winder drums,which comprises a cam movable in response to movement of the shaft awayfrom the drums, follow-up means operatively engaging the cam, a firstcontrol valve actuated by the follow-up means to translate movement ofthe cam to a first fluid pressure signal that is a predeterminedfunction of the roll size, separate fluid pressure inlet means for eachjack, second control valve means receiving the first fluid pressuresignal, translating the same to a pair of second fluid pressure signalseach a function of approximately one-half the roll weight and conveyingone of said second signals to each of said inlet means, and independentfluid pressure supply means for each of said jacks supply additionalfluid pressure to each of said second signals.

8. Mechanism for actuating a pair of independent hydraulic jackscarrying opposite ends of a Winder shaft having a web roll continuouslybuilding up on the shaft and partially supported by under winder drums,which comprises a cam movable in response to movement of the shaft awayfrom the drums, follow-up means operatively engaging the cam, a firstcontrol valve actuated by the follow-up means to translate movement ofthe cam to a first fluid pressure signal that is a predeterminedfunction of the roll size, separate fluid pressure inlet means for eachjack, and second control valve means receiving the first fluid pressuresignal, translating the same to a pair of second fluid pressure signalseach a function of approximately one-half the roll weight and conveyingone of said second signals to each of said inlet means.

References Cited in the file of this patent UNITED STATES PATENTS2,562,028 Foss July 24, 1951 2,609,157 Asmussen et al Sept. 2, 19522,564,546 Hornbostel Oct. 6, 1953 FOREIGN PATENTS 438,640 Great BritainNov. 20, 1935

